Cut-off operating mechanism



I Jan. 12, 1932.

s. M. LANGSTON ET AL 1,840,962

CUT-OFF OPERATING MECHANISM Filed June 25, 1930 8 Sheets-Sheet l BY & 7 M3 144 ATTORNEY 1932- s. M. LANGSTON ET AL 1,840,962

CUT-OFF OPERATING MECHANISM Filed June 25, 1950 8 Sheets-Sheet 2 *4 w INVENTOR Jamaal/1i $049510 BY Karl/Salary ATTORNEY 1932- s. M. LANGSTON ET AL 1,340,962

CUT-OFF OPERATING MECHANISM Filed June 25, 1930 8 Sheets-Sheet 3 m INVENTOR ATTORNEYS Jan. 12, 1932.

s. M. LANGSTON ET AL CUT-OFF OPERATING MECHANISM Filed June 25, 1930 8 Sheets-Sheet 4 &m

Jan. 12, 1932. s. M. LANGSTON ET AL 1,340,962

CUT-OFF OPERATING MECHANISM Filed June 25, 1950 8 Sheets-Sheet 5 l I I I I T R L l war a fi m a SB Q g (44; 7% 7 ATTORNEYS Jam 1932- s. M. LANGSTO.N ET AL 1,340,962

CUT-OFF OPERATING MECHANI SM Filed June 25, 1930 8 Sheets- Sheet 7 ATTORNY- CUT-OFF OPERATING MECHANI SM Filed June 25, 1930 8 Sheets-Sheet 8 amrae a ,s' 0/:

Karl 866:9 W

ATTORN EY Patented Jan. 12, 1932 1 UNITED STATES PATENT OFFICE SAMUEL M. LANGSTON, F WENONAH, AND KARL SIEG, 0F BROOKLAWN, NEW JERSEY,

ASSIGNORS TO SAMUEL M. LANGSTON 00., 0F CAMDEN, NEW JERSEY, A CORPORA- TION OF NEW JERSEY CUT-OFF OPERATING MECHANISM Application filed June 25,

This invention relates to a machine for cutting into sections comparatively stiff material such as double-faced corrugated board during rapid travel of the material. One

'5 type of machine in which the present invention may be incorporated includes a traveling cut-off and clutch and brake device therefor, which are operated in response .to the actuation of a target disposed in the path of the advancing end of the material. By

the term traveling cut-off is meant a cutting mechanism in which the coacting parts for cutting come together to sever the material w-hile advancing. \Vhen a predetermined length of material has passed the cutoff mechanism, the targetis actuated to thereby release the brake, and engage the clutch.

The cut-off mechanism is driven through its cutting position, the clutch is disengaged and the brake is engaged to bring the cutoff to rest after one complete cycle, where it remains until the advancing end of the sheet again reaches the target. The power required to. stop the cut-off mechanism varies with the square of the speed ofthe moving parts which are to be brought to rest. Thus at very high speeds the stopping of the cutoff and its connected parts at the end of each cycle of opefiitiom subjects the machine to destructive stresses shock.

It has been proposed to apply the brake in advance of the desired stopping point and to so adjust the brake that the parts may slip to the final stopping position. This requires readjustment of the brake for each particular speed at which the machine'is operated. Such readjustment must be made frequently under commercial operating conditions and accuracy of adjustment of the 40 brake for each speed is difficult, if not impossible. I

Accuracy and uniformity of operation requires the use of a brake which when applied will stop the parts instantly in a fixed posi- 5 tion. The main objectof the present inven- 1930. Serial No. 483,841.

tion is to permit of the use of such a brake without excessive shock or strain on the mov-' ing arts and without requiring any manual rea justment of the brake for different speeds.

To accomplish this result, the present invention provides means whereby the clutch is disengaged a sufficient time before the brake is engaged so that the moving parts may slow down in the interval between clutch disengagement and brake engagement.

As a further important feature of the in vention, the interval between clutch disengagement and brake engagement is varied in accordance with the speed of the machine. The faster the machine is operating, the longer is the distance between the point of application of the brake and the point of the disengagement of the clutch. Thus the cutoff and connected part will have a greater distance to travel before the brake comes into operation to positively stop the movement of the parts.

The present invention may be employed in connection with the invention of our prior Patent 1,664,119 in which the rest position of the cut-off is fixed and the position of the target isautomati'cally varied in accordance with the speed of travel of the material so that as the speed of the machine increases the position of the target is automatically shifted I in order to insure accurate cutting of sections of predetermined length at different operating speeds.

In our Patent 1,660,844, the shock of stopping and starting the cut-off mechanism is reduced by engaging and disengaging the clutch and brake in the slow speed driving position of an elliptical gear. The present invention may be used in connection with such elliptical gear drive and will act to further reduce the shock of stopping and starting or in some machines may be used as a substitute for such elliptical gear drive.

In the machine shown in our Patent 1,660,-

844, the single cam which disengages the clutch and engages the brake simultaneously is automatically adjusted in respect to the portant feature, one of these cams is automatically adjusted in respect to the other in cut-off device.

accordance with the speed so there is a greater distance between the point of clutch disengagement and brake engagement for high speeds than there is for slow speeds. Our present mechanism may be employed in connection with a machine in which the brake actuating cam is automatically adjusted in accordance with speed variations to secure uniformity of length of cut sections, or may be used with a machine in which the brake actuating cam is fixed on its shaft to give a constant rest position for thecut-off, and a variable point of clutch disengagementp \Vhere used with a non-adjustable brake cam some other means, for instance, the adjustable target of our Patent 1,664,119 maybe employed in order to maintain] uniformity of section length during speed ,variatio'ns.

In the accompanying drawings only one form of our present invention is illustrated,

but obviously variouschanges may bemadc within the scope of the invention as defined in the appended claims.

In the drawings, Fig. 1 is an end view of the machine. Fig. 2 is a front elevation looking in the direction of travel .of the material being cut. Fig. 3 is a top plan view certain of the parts being shown in horizontal section.

Fig. 4 is a longitudinal section 'in. a vertical plane and on a somewhat larger scale on the line 44 of Fig. 3.

Fig. 5 is a side elevation showing details of the cam mechanism which operates the Fig. 6 is a horizontal section showing details of the cam adjusting mechanism.

Figs. 7 and 8 are sections taken on lines 7-7 and 8-8 respectively of Fig. 5, and

Fig. 9 is a plan view of the drive mechanism. The traveling cut-ofi' illustrated is that disclosed in the Langston Patent 1,359,076, but the present invention may be employed in connection with various other types adapted for intermittent operation through successive cycles. As shown, a pair of upstanding arms 10 (Figs. 1 and 2) are pivoted at opposite sides of the machine on a transverse rock shaft or pair'of pivot pins 11,

transverse beam 12 which carries a knife or cutting member 13. Each arm 10 also carr es a pivot pin 14 in which is mounted a members which carry the two knives 13 and 17 are connected together by the pivot pins 14 it will be apparent that the back and forth movement of the knife 13 in the direction of'travel of the sheet will be accompanied by a corresponding back and forth movement of the knife 17 As the knife 17 also has a vertical movement its resultant palthof travel becomes substantially elliptica.

lever 15. The pair of levers 15 are spanned at their upper front ends by a transverse For imparting the desired operating movepath.

For guiding the sheet between the knives and for preventing the edge of the sheet from lifting with the knife 17, there are provided a pair of guide, plates 22 and 23 secured to the beam 12. The plate 22 projects downwardly and rearwardly, and the plate 23, upwardly and rearwardly, as shown in Fig. The lower front end of the upper guide plate 23 may engage a support 24 carried by the beam 12 and spaced from the knife 13, and the rear edge may be carried by supports 24 carried by the arm 10. Thus the sheet is kept within comparatively narrow limits between the knife 13 and the upper guide plate 23. The support 24 may be constructed to form or carry a wiper for cleaning the knife 17.

- For supporting the material in advance of the cutters there is provided a table or platform 25 which is mounted on brackets or side frame members 26. These also carry a feeding mechanism which includes a pair of rollers 27and 28, the upper roller 28 being carried by pivoted arms 29 so that it may rest by its own weight on the sheet of material, The lower roller 27 may be driven in any suitable manner, as for instance by a sprocket chain 30 and a pair of sprocket wheels 31 and 32, the

- has prepared, treated or manufactured the sheet material which is to be cut up, the feed rollers 27 and 28 may be omitted from the cut-off mechanism, and the material fed to the cut-off mechanism solely by the other machine mounted in advance thereof. Hereinafter, in referring to sheet feeding mechanism we mean either the rollers 27, 28, or any other mechanism which may serve the same purpose even though said mechanism may be disposed on a separate machine inthe path of movement of the material. r

In operating the cut-off mechanism the shaft 33 is driven at a speed directly proportional to the speed of the machine which manufactures or treats the sheet material to be cut up. It may be driven directly from the same source of power, or may be directly driven from the other machine. As shown in Fig. 3, it is geared-to a shaft 34 extending lengthwise of the machine at one side, and constituting the main drive shaft from which all of the pieces of apparatus operating on the-sheet are driven.

For intermittently operatin'g'the shaft 18 from the constantly driven shaft 33 there is provided between these shafts an intermediate shaft 37 geared to one of the first mentioned shafts, and having clutch connections to the other. In order to efiect the desired high speed of cutting and low speed at the time of brake engagement, the shaft 37 is connected-to the shaft 18 by a pair of elliptical gears 38 and 39 which are so positioned in respect'to the crank arms 20 that the cutting will take place when the shaft 18 is in approximately the angular position at which the .elliptical gears drive the moving part the fastest, and the brake and clutch are shifted when the gears drive the moving parts the slowest set forth and claimed in our Patent 1,660,844.

The shaft 37 is provided with a flywheel 40 relatively rotatable in respect thereto, and having a sleeve driven from the shaft 33 by a pair of gears 41, 42. The relative sizes of these gears are such as to give the flywheel 40 the desired speedwithrespect to the shaft 33, and to thereby control the speed of the cutter with respect to the speed of the machine. As

' shown in Fig. 3, the shaft 34 drives the shaft 33 at lower speed through a'pinion and gear, and the shaft 33 drives the flywheel 40 at still lower speed-as the pinion 41 is smaller than the gear 42.

The machine has means for positively operating the cut-off operating shaft 37 from the fly-wheel 40 through one complete revo- 'lution, then disengaging said cut-off operating shaft from its assoclated drlving means and applying a brake mechanism to said shaft. For this purpose, a clutch is mounted inside of the fly-wheel 40 and includes brake t0 the shaft 37 and actuated by a cone 44 slidable on said shaft. The brake is very similar to the clutch, except that the clutch shoes 45 of said brake are expanded in a non-rotatable casing 46 when a co-operating cone 47 is moved axially. The two cones 44 and 47 are connected together by a sleeve 48 and face in opposite directions between the clutch and brake so that they move simultaneously in one direction to engage the brake and disengage the clutch, and in the opposite di-' rection engage the clutch and disengage the brake. However, these two cones 44 and 47 are so spaced as to permit the disengagement of the clutch 40 without effecting the engagement of the brake 46 or vice versa.

shoes or clutch members 43 (Fig. 4) keyed 1 Disposed within the sleeve 48 is a coil 3 spring 49 confined between a shoulder on said sleeve, and a collar 50 on'the shaft 37 so that when the sleeve is released, said spring automatically shifts said sleeve towards the right as viewed in Fig. 4, to completely disengage the brake and completely engage the clutch. Means are provided for forcing the sleeve endwise against the action of the spring 49, said means including a trip mechanism so mounted that when released said spring acts to force the sleeve 48 to clutch engaging position.

A collar 51 is mounted for axial movement with the sleeve, and hasan end thrust bearing between it and said sleeve toreduce friction during compression of the spring. The collar 51 is provided on opposite sides thereof with trunnions or other pivotal connections to a gimbalring 53 (Fig. 5) which is larger than the collar 51 so that it may tilt, and its upper and lower edges may move through greater distance than the collar 51 in the eneral direction of the length of the shaft This gimbal ring 53 is provided with a stop mechanism on one side thereof and an actuating mechanism at the other. The actuating mechanism includes a shaft 54 geared to the shaft 18 through the agency of bevel gears 55 and 56 so that these two shafts will rotate at the same angular velocity and stop and start together. As previously noted, the separate actuating of the clutch and brake forms an important feature of the present invention.

In order to control the operation of the clutch device, this shaft 54 has rotatably mounted with respect thereto a clutch control cam 57 cooperating with a cam roller 58 carried-on the end of a lever arm 59 carried by a' rock shaft 60. This cam 57 is fixedly mounted to a bevel gear 61 so as to be rotatable therewith, and at the same angular speed as the speed of the shaft 54, but in the opposite :9 ment of the shaft 54.

In order to control the applicationof the brake mechanism there is provided a brake control cam 67 fixed on the shaft 54' and cooperating with a cam roller 68 mounted on.

a second lever arm 69, mounted on the rock shaft 60. The rock shaft has a lower arm 70 pivoted to the top portion of the gimbal ring 53. The arm carries an extension 71 which is provided with a coil spring 7:2 serv- 53 ing to urge the roller 68 into engagement with the cam 67. The stop mechanism includes an arm 73 mounted on a rock shaft 74, said arm being angularly movable into or out of the path of movement of an arm 7 5 fixed to the lower side of the gimbal ring 53.

Asshown, particularly in Fig. 4, the parts are in the position which they occupy after the clutch has been disengaged andbefore 6 the brake is engaged. v The cam 57 has raised its roller but the cam 67 has not come into operation. The gimbal ring 53 and the sleeve are in middle position, ready to be moved toward the left. The lower side of the gimbal ring cannot move toward the right because the arm 75 abuts against the arm 73. The upper side of the gimbal ring cannot move toward the right because the roller 58 on the arm 59 is rested on the high part of the cam 57. The cam 67 continues Q to move clockwise lifting the roller 68 and 'forcing the brake into engagement. The

cutofl is then instantly stopped.

lVhen the end of the advancing sheet strikes the target (not shown) the rock shaft 74 turns counterclockwise from the position shown in Fig. 4 until the stop 73 moves out of the path of the arm 75. The gimbal ring may then swing toward theright under the influence of the spring 49. The brakehs dis- [o engaged, the clutch is engagedand the cutoff starts in its cycle. This, of course, rotates the cam shaft 54 to take the cams out of operative position.

While thefcut-ofi' mechanism is operating,

the roller'58 is riding along thelow'portion of the cam 57, the arm 71 is moved to a position. below that indicated in Figs. 4 and 7,

gimbal ring 53 is tilted, and the clutch 40 a is in engaging position. As soon as the high point of the cam 57 isadvanced into cooper:-

ative relationship with theroller 58, it'will cause this roller to rise effecting-thereby a clockwise rotation of the shaft 66. This will 7. cause the lower part 70 of the bell crank i" which is rigidly connected to theshaft 60 to shift towards the left to the position shown in Fig. 4, and move the gimbal ring and sleeve 48 a sufficient distance to disengage the clutch but the raised portion of this cam 57 is not high enough to move the sleeve 48 sufiiciently to the left to apply the brake. While this raised portion of the cam 57 is riding underneath the roller 58, the high point of the cam 67 is approaching from the opposite direc-.

wise stop. During the cycle, the knives have severed the sheet and the new end of the sheet or other material will continue to advance. VVhenit reaches a predetermined point controlled by a target'or other apparatus, the shaft7 4 is again caused to oscillate to a limited extent to trip the gimbal and the cycle is repeated. v

The shaft 54. then starts to rotate, and the high point of the cam 67 passes from beneath its cooperating roller. 68 permitting the spring 7 2 to swing the bell crank lever 70 and move the end thereof which is connected to the gimbal ring 53 towards the right. During this movement, the trunnions 52 act as a fulcrum for the gimbal ring, and the arm moves towards the left to a point beyond the end of the arm 73. While in this position, the shaft 74 is oscillated in the opposite direction into its initial or normal position, shown in Fig. 7. While these move-.

ments have been taking place, the shaft 54 has been continuously rotating and when approaching the end of a single revolution,

which corresponds to a single complete revolution of the shaft 18 and the movement of the cutter through one cycle of operation, the high part of the cam 57 again engages the roller 58 to lift the latter and cause the lower end of the bell'crank lever 70 to swing towards the left. In this position, the arm 73,

forms a fulcrum for the gimbal ring 53 and .the movement ofthe upper side of the ring T sheet measuring device or other mechanism may be employed with suitable operative connections to the shaft 74. It is preferred to employ the target and associated mechanism illustrated in U. S. Patent 1,664,119.

A mechanism is provided for positively returning the shaft 74 to normal position before the completion of a single revolution thereof. This mechanism as illustrated (Fig. 2) includes an arm 7 6 on the shaft 74 and a lever 77 pivoted intermediate of its ends with one end so positioned as to engage with the arm 76 and swing it in counterclockwise direction when the lever swings in the opposite direction. The upper end of this lever has a roller 78 in,engagement with a cam 79 on the shaft 54, so that said cam 79 rotates in unison with the cam 57. The two cams 57 and 79 are so timed that the cam 79 operates on the lever 77 to swing the arm 73 in the position shown in Fig. 7, when the arm 75 of the gimbal ring 53 is in the lefthand position of its range of movement.

The shaft 74 is preferably provided also with a third arm 7 9 (Fig. 9) which is connected to a spring79 which swings the shaft 74 counterclockwise in a powerful and rapid manner when said shaft is released by the target or other mechanism at the advancing end of the sheet.

In Fig. 9 there is illustrated somewhat conventionally the ordinary Reeves drive for selectively varying the speed of the cut-off mechanism as well as the machine that feeds the material to said cutoff. The power is delivered to the Reeves drive through a shaft 80 and froni the Reeves drive to the machine for feeding the material as well as the cut-off mechanism through the shaft 81. These two shafts are parallel and have cone pulleys 82 and 83 connected by a belt 84. By rotating a control handle 85'the shaft 86 is rotated.

This, in turn, rotates a shaft 87 which may also have a control handle at the opposite side of the machine if desired, and which drives a screw shaft 88. The latter has right and left hand threaded portions engaging I nuts which latter engage levers :89 and 90 1 The details of this construction form no portion of 7 our invention. This mechanism commonly known as a Reeves drive is illustrated merely as one practical and commercially satisfactory means for varying the speed of the cut-off mechanism and the machine for feeding the material.

Any other suitable means might be employed for varying' the speed of these machines upon the rotation of the control handle. If the drive be an electric motor, for instance; the shaft -with the speed of the machine.

88 may be rotated to operate the rheostat or other circuit controller of the motor.

One of the important features of the present invention is the means for varying the time interval between the disengagement of the clutch and the engagement of the brake in accordance with the speed of the machine.

This means is so operated that when the speed of the machine is increased, the time interval between the disengagement of the clutch and the engagement of the brake is correspondingly increased to permit the operating parts to dwindle to a safe arrestable speed. For this purpose, the rotation of the shaft 86 is preferably transmitted to a shaft 91 through the agency of miter gears 92 and 93. Mounted on said shaft 91 is a sprocket wheel 94 which is operatively connected with a sprocket wheel 95 by means of a chain 96. This sprocket wheel 95 is mounted on one end of a shaft 97, the other end of which carries a bevel gear 98 which meshes with a bevel gear 100 carried at one end of a shaft 101. This shaft 101 has mounted thereon a worm gear 102 which meshes with a worm wheel 103. This worm wheel 103 is secured to the difierential casing 66 so that the rotation ofv this worm wheel is transmitted to this differential casing 66.

When the shaft 86 isrotated in response to the manipulation of the control handle 85 to increase or decrease the speed of the machine, the shaft 97 will be correspondingly rotated to advance or retard the position of the cam 57 with respect to the position of-the cam 67 through the resultant rotation of-the dfferential casing 66. In this manner, the relative position of these two cams are varied in accordance with the speed of the mechanism so that the time interval between the disengagement of the clutch and the application of the brake will be increased in accordance This increased interval of time as thespeed of the machine increases permits the brake to be applied without any corresponding increase in the shock due to the increase in the operating speed.

It should be noted that the cut-off mechanism is positively stopped through the application of the brake at a fixed point in the cycle of operation irrespective of the speed of travel of the material to be cut, and the position of disengagement of the clutch, ad-

vanced or retarded in accordance. with said speed of travel of the material. however, the cut-off mechanism may be disengaged from the clutch mechanism at a variable point in the cycle of operation depending upon the speed of travel of the material to be cut, and the stop position may be varied in accordance with the speed of travel of the material. This can be effected by automatically varying the position of both cams 57 and 67 one in one direction and the other in If desired, I

the opposite direction for a given speed change- The distance of such movements for the two cams should be difierent, the clutch releasing cam having a greater range than the brake applyin cam because the adjustment of one shoul vary as the square of the speed and the other only directly as the speed.

We have illustrated the two separate cams rotatable in opposite directions on the shaft, but this is only to adapt the invention to a specific form of machine now on the market be understood that various omissions, substitutions and changes in the forms and details of the device illustrated and in its operation may be made by those skilled in the art without departing from the spirit of the invention. c Having thus described my invention, what I claimis new and desire to secure by Letters Patent is:

1. A sheet cutting device, including a cutoff mechanism, means for disengaging said cut-off mechanism from a source of driving power, means for positively stopping said cut-ofi mechanism, and means for varying the time intervalbetween the actuation of said disengaging means, and said positive stopping means in accordance with the speed of travel of the material to be cut.

2. A sheet cutting device, including a cut- 01ft mechanism, means for disengaging said cut-ofl mechanism from a source of driving power,means for positively stopping said cut-01f mechanism at a distance beyond the point of actuation of said power disengaging means, and at a .fixed point in the cut-off cycle of operation, and means for varyingthe point of power disengagement of said cut-ofl' mechanism in accordance with the speed of travel of the material to be opt.

3. A sheet cutting device, including'a cutofl mechanism, a shaft connected thereto, a

pair of cams on said shaft, means res onsive to the actuation of one of said cams or disengaging said cut-oif mechanism from a source of driving power,-m-eans responsive to the actuation of the other cam for positively stopping said cut-off mechanism a predetermined time after, the disengagement of said driving power, arid means for varying the relative angular position of one cam in respect to the other in accordance *with the variation in the speed of travel oi the material to be cut. p f

4. A sheet cutting device including a cutoff mechanism, a pair ofcams, means responsive to the'actuation of one of said cams for disengaging said cut-oil" mechanism from a tively stoppingsaid'cut-ofl mechanism a predetermined time after the disengagement of said driving power, and means for varying the relative position of said cams in accordance with the speed of travel of the sheet to be cut, whereby the time interval between the disengagement of said driving power and the correspondinglyyaried.-' c c '5. sheet} cutting-device, including a cutoff mechanism-fa shaft, a 'first cam fixedly mounted on saidishaft, a second cam loosely mounted on said-"shaft,-meansqfor rotating actuation of said positive stoppingmeans is .same cams in unison, means for varying the relative angular position of said cams in accordance with the speed of travel of the material to be cut, and means responsive to the actuation of said cams for alternately disengaging s aid cut-cit mechanism from a driving source of power and positively stopping said cut-off mechanism. v

6. A sheet cutting device including a cutoff mechanism, a pair of cams operated in unison, means responsive to the actuation of one of said cams for disengaging said cut-off mechanism from its driving source of power, means responsive to the actuation of the other cam for positively stopping said cut-0E mechanism a predetermined time after the disengagement of said cut-ofi' mechanism, and means for varying the relative position of said cams in accordance with the speed of travel of said material. 7

7. A sheet cutting device, including a cutoff mechanism, af pair of cams, a clutch adapted to disconnect said cut-01f mechanism from a source of driving power, a brake mechanism adapted to positively stop the operation of said cut-oil mechanism, means operable in response to the actuation of one of said cams .for disconnecting said cut-oil mechanism from said clutch, means operable 1n response interval between the actuation of said cams is correspondingly varied;

8.- A sheet cutting device including means for continuouslyadvancing a sheet of material, a traveling cut-off mechanism, a. clutch adapted to operatively connect said cut-off with a source of driving power, a brake mechanism adapted to positively stop the operation of said cut-off mechanism, a mem- 7 her connecting said clutch and brake mechanism, means'for moving said membera limiteling cut-ofi' mechanism, a clutch adapted to operatively connect said cut-0E with a source of driving power, a brake mechanism adapted to positively stop the operation of said cut-off mechanism, said clutch and brake mechanism being mounted in coaxial relationship, a slidable member interposed between said clutch and brake mechanism, a cam for moving said member to disengage the clutch and a second cam for moving said member to engage said brake.

I 10. A sheet cutting device including a cut- 1 off mechanism, a pair of cams, a clutch adapted to operatively connect said cut-ofi' mechanism with a source of driving power, a brake mechanism adapted to positively stop the operation of said cut-off mechanism, a slidable member for operating said clutch and said brake mechanism, means responsive to the actuation of one of said cams for shifting said slidable member out of engaging relationship with the clutch, but not sufficient to engage the brake mechanism and means responsive to the actuation of the other cam for further shifting said slidable member into N engaging relationship with the brake mechanism.

11. A sheet cutting device including a cutoff mechanism, a pair of cams, a clutch adapt-- ed to operatively connect said cut-01f mechanism with a source of driving power, a brake mechanism adapted to positively stop the.

operation of said cut-off mechanism, a member connected to said clutch and brake mecha nism, means responsive to the actuation of one of said cams for shifting said member out of engaging relationship with said clutch, but

not sufficient to engage the brake mechanism, means responsive to the actuation of the other cam for further shifting the slidable member into engaging relationship with the brake mechanism, and means for varying the relative positions of said cams in accordance with the speed of travel of the material to be cut, whereby the interval between the disengagement of said clutch and the engagement of said brake is correspondingly varied.

12. In combination, means for continuously advancing material to be cut into sections, a tr veling cut-off, a clutch for driving said cut-off, a brake, a shaft operatively connected to said cut-off, a pair of cams on said shaft, means operated by one cam for disengaging said clutch, means operated by the other cam for engaging said brake, a differential for rotatably adjusting one of said cams in respect to the other, means for varying the speed of travel of said material and means connected to said speed varying means for operating said difierential.

13. In combination, a

of cams on said-shaft, means operated by one cam for applying transmission of power to said 'cut-ofi', means operated by the other cam for positively stopping said cut-01f, means for varying the speed of travel of the mate- 6 rial to be cut off, andfmeans operatively traveling cut-off, a' shaft operatively connected thereto, a pair connected to. said last mentioned means for rotatably adjusting one cam in respect to the other.

14. In combination, means for continuously advancing a sheet of material, a traveling cut-ofi' adapted to operate through successive cycles, means for disconnecting said cut-off from a source of power at one point in the cycle, means for positively stopping said cut-ofi' at another point in the cycle, and means for varying the distance between said points in the cycle.

15. In combination, means for continuously advancing a sheet of material, a traveling cut-off adapted to operate through successive cycles, means for disconnecting said cut-off from a source of power at one point in the cycle, means for positively stopping said outoff at another point in the cycle, and means for advancing or retarding the point of clutch disengagement in respect to the point of brake engagement in accordance with the speed of travel of the material to be cut.

16. A sheet cutting machine, including a traveling cut'off operating through a series of successive cycles, a cam for eife cting the disengagement of the cut-off from the source of power, a cam for effecting the positive stopping of the cut-off mechanism, and means for adjusting one cam in respect to the other.

17. A machine for cutting continuously traveling sheet material into sections, including a traveling cut-oil", a shaft connected thereto, a cam on said shaft and relatively rotatable in respect thereto, a gear connected to said cam, a separate gear secured to said shaft a differential housing having a gear meshlng with both of said gears, and means for rotating said housing to effect a relative rotation of said cam in respect to said shaft.

18. A machine for cutting continuously traveling sheet material into sections, including a traveling cut-01f, a shaft connected thereto, a cam on said shaft and relatively rotatable in respect'thereto, a gear connected to said cam a separate gear secured to said shaft, a differential hpusing having a gear meshing with both of said gears, means for varying the speed of travel of the material to be cut, and means for rotating said differential housing during the variation in the speed of travel of the material.

- 19. In combination means for continuously advancing material, mechanism for cutting the material during the advancing movement, means for disengaging said mechanism from a source of drlvlng power, means for positively stopping said mechanism and means for varying the time interval between the actuation of said disengaging means and said stopping means in accordance with the speed of travel of the material.

- 20. In combination means for continuously advancing a sheet of material, a cutting mechanism adapted to operate through successive cycles, means for disconnecting said rhecha Iiism from a source of power at one point in the cycle, means for positively stopping said mechanism at another point in the cycle,

and means for varying the distance between said points in the cycle.

Signed at Camden, in the county of Camden and State of New Jersey, this 20th day 0fJune,'1930.

S'AML. M. LANGSTON.

KARL SIEG. A

Cal 

